US3962933A - Drive system, particularly for ships - Google Patents

Drive system, particularly for ships Download PDF

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Publication number
US3962933A
US3962933A US05/544,189 US54418975A US3962933A US 3962933 A US3962933 A US 3962933A US 54418975 A US54418975 A US 54418975A US 3962933 A US3962933 A US 3962933A
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US
United States
Prior art keywords
coupling
clutch
shaft
input
elastic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/544,189
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English (en)
Inventor
Herbert Wedler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vodafone GmbH
Original Assignee
Mannesmann AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19742405419 external-priority patent/DE2405419C3/de
Priority claimed from DE19742407981 external-priority patent/DE2407981A1/de
Application filed by Mannesmann AG filed Critical Mannesmann AG
Application granted granted Critical
Publication of US3962933A publication Critical patent/US3962933A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/30—Transmitting power from propulsion power plant to propulsive elements characterised by use of clutches
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19074—Single drive plural driven
    • Y10T74/19079—Parallel
    • Y10T74/19084—Spur

Definitions

  • the present invention relates to heavy duty drive systems e.g. for ships and move particularly to improvements in such systems which include a drive engine or motor, a transmission gear, e.g. a reducing gear, an elastic coupling and interconnect means between the transmission gear input shaft and the motor or engine output shaft.
  • a drive engine or motor e.g. a Bosch gear
  • a transmission gear e.g. a reducing gear
  • an elastic coupling and interconnect means between the transmission gear input shaft and the motor or engine output shaft e.g. a reducing gear
  • a drive system of that type is for example disclosed in U.S. Pat. No. 3,669,230.
  • the system serves in particular for occasionally driving the propellor shaft of the ship via a resilient clutch, but an auxiliary generator is continuously driven via a power and torque branching system included in the transmission path from the engine to the reducing gear.
  • the resilient clutch has an inner ring as rotary output which is seated on a pinion (input) shaft for the reducing gear, whose output drives the propellor.
  • the clutch is used for power branching to obtain the aforementioned dual drive function.
  • This branching train includes also an elastic coupling having concentric input and output parts which are interconnected by means of a rubber elastic element.
  • the present invention therefore, relates also to improvements in a torque transmission system which permits such power branching.
  • a heavy duty system of that kind has bearings for the engine or motor shaft and bearings for the transmission shafts, gears, etc.
  • the interconnect system between them must be supported by one or the other.
  • the known systems require that the motor or engine shaft and its bearings support the interconnect structure between transmission and motor or engine to a considerable extent. As to this it has to be observed, that some or even significant radial displacement may occur between reducing gear and motor shaft. Such radial displacements between engine and reducing gear will be observed when the motor or engine itself is elastically mounted or if the foundation itself has some degree of softness.
  • the additional elastic coupling is interposed between the output of the motor coupled coupling and the input element of the clutch.
  • the input element of the clutch is rigidly secured to a bell shaped or dish shaped element that is journalled on the transmission shaft or the transmission casing. Since the transmission shaft is journalled in the transmission casing, one can also say that this bell or dish shaped element is either directly or indirectly journalled to the casing. Specifically, in the latter case, the bell or dish shaped element is secured to a hollow shaft for driving it; this hollow shaft is traversed by the transmission input shaft; is separately journalled in the casing; and is connected to a gear for transmission of rotational power to an auxiliary equipment shaft.
  • the suspension of the clutch input on a journalled hollow shaft by means of rigid connection to and with a bell shaped structure is a feature having its own significance particularly with regard to the journalling and support of the input element for the clutch. Even without additional elastic coupling, none of the clutch parts nor the output of the motor coupled coupling will bear on the motor or engine shaft.
  • the input element of the clutch is connected through the additional elastic coupling to a bell shaped structure which is either journalled in the casing or on the transmission shaft; i.e. either directly or indirectly journalled in the casing because the transmission shaft itself is journalled in the casing also here.
  • the output element of the motor coupled coupling and the input element of the clutch may be rigidly interconnected in that case and are, therefore, cardanically suspended together.
  • the elastic elements of the additional coupling are preferably arranged in a circle which is larger than the circle along which elastic elements are arranged inside of the resilient shift clutch.
  • the several elastic elements are preferably rubber elastic sleeves, held in an annulus which is secured to the input element of the clutch and which are traversed by bolts leading to a disk which is either secured to the output element of the motor coupled coupling or to the bell shaped structure.
  • FIG. 1 is a cross-section through a drive system showing a first example for the preferred embodiment of the invention, wherein particularly the intermediate coupling is interposed in the power and torque transmission path from an elastic coupling to the elastic clutch;
  • FIG. 2 is a similar view but showing the intermediate coupling as cardan suspension for the input of the clutch as well.
  • the system includes in both cases a motor or engine 1 having a rotor output flange 2 which is connected directly to the motor shaft and supported by the shaft bearing, accordingly.
  • the input of an elastic coupling 3 which is not of the connect-disconnect type, is secured to flange 2.
  • the output of coupling 3 in turn drives a resilient connect-disconnect or shift clutch 4 whose output in turn is connected to drive a speed reducing gear 5, serving as transmission gear to the load proper, which is a propellor shaft (not shown).
  • the clutch 4 has a driving output established by a ring or annulus 15 which sits on the pinion shaft 16, the latter being the input shaft for the reducing gear 5.
  • the gear 5 includes a casing 18, and pinion shaft 16 is journalled in the casing by means of suitable bearings 17.
  • Shaft 16 carries a pinion which meshes a gear (not shown) which in turn is drivingly connected to the propellor shaft (not shown, see for example, U.S. Pat. No. 3,669,230).
  • a secondary output shaft 24 is journalled by means of bearings 26 in an extension of the casing 18. This shaft is provided, for example, to drive a generator and/or other auxiliary equipment. Shaft 24 carries a pinion gear 23 which is driven by a gear 22.
  • Gear 22 is secured to a hollow shaft 21 which is also journalled in casing 18 by means of bearings 25.
  • Shaft 21 is concentric to shaft 16 and the latter traverses the former with play, so that shafts 21 and 16 can rotate independantly from each other. It should be noted however, that shaft 21 could be journalled on shaft 16, so that shaft 21 would be journalled indirectly in casing 18 in such a case. In any event, the shafts 16 and 21 are journalled for independent but concentric or coaxial rotation.
  • both shafts are driven from clutch 4 serving as a power branching device, in that the primary input of the shift clutch provides also the rotational (continuous) input for shaft 21, while shaft 16 requires an engaged clutch for rotation through the power, as applied to and transmitted by the clutch.
  • coupling 3 has an inner ring 7 and an outer ring 9, and these rings are interconnected by a rubber elastic layer or elements 8.
  • the coupling as such is the same in both Figures, but input and output connections differ. Nevertheless, the input element of the resilient coupling 3 is connected directly (and supported by) the motor or engine shaft. The output or driving part of coupling 3 is not journalled on or otherwise connected to the motor or engine shaft except through the resilient means 8.
  • FIG. 1 shows a predominantly flat annulus 6 actually having axially displaced inner and outer flanges.
  • the outer flange connects to motor flange 2 while the inner flange is connected to annulus 7.
  • ring 7 in Figure 1 is the input of coupling 3.
  • the output of the coupling is provided via annulus 9 to which is connected a ring 34; further connections are made through that ring.
  • FIG. 2 shows a predominantly cylindrical element 6', having axial end flanges respectively secured to motor flange 2 and to the outer ring 9 of the coupling 3.
  • the input for the coupling is provided here through the outer annulus or ring 9.
  • a predominantly flat annulus 34' serves here as output connector for the coupling taking the output from inner ring 7.
  • clutch 4 is constructed as a pneumatically operated, elastic-resilient, double cone, friction clutch.
  • the clutch has an outer, driving portion 10 constructed as short cylinder casing with two conical ends. Conicity as to the outer surface is not essential (but convenient). Decisive is that the internal surfaces of element 10 have conical contour.
  • the driven part, element 11 of the clutch is comprised of two conical members 12 having friction lining for frictional engagement with the said conical inner surfaces of the two conical portions of part 10.
  • the two parts 12 are axially displaceable with respect to each other for engagement with and disengagement from part 10.
  • the two parts 12 are constructed to provide for an annular, piston-cylinder arrangement 13 which when pressurized causes the parts 12 to spread axially for clutch engagement. Upon venting the piston chamber, the clutch parts disengage.
  • Parts 12 and 13 constitute the or part of the operating means for this shift clutch.
  • Parts 12 are mounted to inner ring 15 of clutch 4 by means of resilient members 14 which permit axial displacement of parts 12 but both of them are always drivingly connected to ring 15.
  • These resilient-elastic elements are constructed as sleeves which are inserted in apertures of disks which in turn are secured to annulus 15. The sleeves are traversed by bolts which are secured to the driven clutch parts 12.
  • Elements 27 are known, rubber elastic sleevespring elements, i.e. they consist of annular rubber sleeves traversed by a bolt 31.
  • the clutch elements 14 are of similar construction (see e.g. U.S. Pat. No. 3,804,220).
  • outer annulus 9 is the driving output of the coupling 3 and that annulus is to be cardanically suspended as per the rule of this invention.
  • the driving input annulus 7 of coupling 3 is rigidly flanged to the motor flange 2.
  • the intermediate coupling 30 is interposed between coupling 3 and clutch 4, or, more specifically, in the power and torque transmission path between coupling output 9 and clutch input 10.
  • Coupling 30 has a carrier annulus 28 with apertures along the periphery in which are inserted the rubber sleeves 27.
  • the bolts 31 traversing the elastic elements 27 are connected to two rings or disk 32, 33; constituting the input portion of that additional coupling; 28 is the output thereof.
  • clutch part or input element 10 is connected additionally to hollow shaft 21 by means of a bell or dish shaped disk 20. That connection is a rigid one. Since shaft 21 is journalled in casing 18, disk 20 and part 10 is journalled therewith.
  • Motor 1 drives its flange 2 which in turn drives disk 6 and torque is transmitted from there via annulus 7, elastic elements 8, annulus 9, ring 34, coupling 30 to clutch input part 10.
  • the clutch branches the power and torque.
  • a permanent connection and torque transmission is provided through disk 20 to hollow shaft 21 driving auxiliary equipment shaft 24 via gears 22, 23.
  • torque is additionally transmitted from part 10 to clutch part 11 driving shaft 16 which in turn will drive the propellor shaft via gear 19.
  • the coupling 3 has its outer ring 9 connected to motor flange 2 via cylinder element 6', while the inner ring 7 provides the driving output.
  • this inner ring that is being cardanically suspended.
  • the cardan suspension includes also the clutch part 10.
  • FIG. 2 shows also the disk 20 which is secured to the journalled hollow shaft 21.
  • Another bell shaped element 29 is axially flanged to the large end of disk 20, and element 29 has an axial end flange 33' performing the analogous function as ring 33 in FIG. 1, as far as the intermediate coupling 30 is concerned.
  • the elastic elements 27 in this construction are held in the peripherally arranged apertures of a disk 28' which is interposed in axially split portions of clutch part 10, being secured to both of them.
  • the disk 28' is specifically disposed in the plane which includes the cardan pivot for the clutch. The plane of course extends transverse to the axis of rotation of the clutch and coupling system.
  • the other disk 32, of coupling 30 is bolted to disk 33' as before.
  • the cardan mount and suspension is completed by rigid connection between annulus 7 and clutch part 10 under interpositioning of the disk 34'.
  • the cardan mount for parts 7 and 10 (including 34') is, therefore, constituted also here by the elastic-resilient layer 8 of the coupling 3 and by the elastic-resilient elements 27 of coupling 30.
  • the power and torque branching occurs also in this example, except that the permanent connection between part 10 (as driven via coupling 3) and hollow shaft 21 runs through the resilient elements of the intermediate coupling 30. That coupling 30 is not effective in the path for transmission of torque to the pinion and propellor shafts.
  • the elements 27 are arranged in both examples along a circle having a diameter which is larger than the diameter of the circles along which clutch elements 14 are arranged.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Gear Transmission (AREA)
US05/544,189 1974-02-01 1975-01-27 Drive system, particularly for ships Expired - Lifetime US3962933A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DT2405419 1974-02-01
DE19742405419 DE2405419C3 (de) 1974-02-01 1974-02-01 Schiffsantriebsanordnung mit einer schaltbaren Kupplung und einer nicht schaltbaren elastischen Kupplung
DE19742407981 DE2407981A1 (de) 1974-02-15 1974-02-15 Antriebsanordnung fuer schiffe
DT2407981 1974-02-15

Publications (1)

Publication Number Publication Date
US3962933A true US3962933A (en) 1976-06-15

Family

ID=25766580

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/544,189 Expired - Lifetime US3962933A (en) 1974-02-01 1975-01-27 Drive system, particularly for ships

Country Status (7)

Country Link
US (1) US3962933A (en, 2012)
JP (1) JPS50107688A (en, 2012)
DD (1) DD116177A5 (en, 2012)
ES (1) ES434101A1 (en, 2012)
FR (1) FR2259748B3 (en, 2012)
NL (1) NL7500087A (en, 2012)
SE (1) SE396339B (en, 2012)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678439A (en) * 1984-07-17 1987-07-07 Blohm & Voss Ag Engine installation for use in a ship
US6033271A (en) * 1995-10-04 2000-03-07 A. Friedr. Flender Ag Ship drive with a driving engine and a directly driven propeller shaft
US6328547B1 (en) * 1999-04-08 2001-12-11 Nakanin Co. Ltd Rotary pump
EP1889782A1 (en) * 2003-10-02 2008-02-20 Yanmar Co., Ltd. Power generation system of ship
EP1669287A4 (en) * 2003-10-02 2008-09-03 Yanmar Co Ltd SHIP POWER GENERATION SYSTEM
CN109854725A (zh) * 2019-04-02 2019-06-07 哈尔滨广瀚动力传动有限公司 一种应用于shrt机组的变速离合器的输出轴的布置形式

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2514029B2 (de) * 1975-03-29 1977-07-21 Elastisch gelagerter kupplungsteil
JPS5570396U (en, 2012) * 1978-11-10 1980-05-15
DE3331480A1 (de) * 1983-09-01 1985-03-28 F. Tacke Kg, 4440 Rheine Schiffsantriebsanlage
DE8711216U1 (de) * 1987-08-18 1987-10-01 Jastram-Werke GmbH & Co KG, 2050 Hamburg Querstrahlruder, insbesondere Bugstrahlruder, für Schiffe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3727431A (en) * 1971-10-12 1973-04-17 Twin Disc Inc Flexible torsional coupling
US3777865A (en) * 1972-03-20 1973-12-11 J Walter Combined clutch and flexible coupling
US3791497A (en) * 1972-07-28 1974-02-12 Lohmann & Stolterfoht Ag Elastic shaft clutch
US3813897A (en) * 1972-05-17 1974-06-04 Mannesmann Meer Ag Resilient shaft coupling for ready assembly and disassembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3727431A (en) * 1971-10-12 1973-04-17 Twin Disc Inc Flexible torsional coupling
US3777865A (en) * 1972-03-20 1973-12-11 J Walter Combined clutch and flexible coupling
US3813897A (en) * 1972-05-17 1974-06-04 Mannesmann Meer Ag Resilient shaft coupling for ready assembly and disassembly
US3791497A (en) * 1972-07-28 1974-02-12 Lohmann & Stolterfoht Ag Elastic shaft clutch

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678439A (en) * 1984-07-17 1987-07-07 Blohm & Voss Ag Engine installation for use in a ship
US6033271A (en) * 1995-10-04 2000-03-07 A. Friedr. Flender Ag Ship drive with a driving engine and a directly driven propeller shaft
US6328547B1 (en) * 1999-04-08 2001-12-11 Nakanin Co. Ltd Rotary pump
EP1889782A1 (en) * 2003-10-02 2008-02-20 Yanmar Co., Ltd. Power generation system of ship
EP1669287A4 (en) * 2003-10-02 2008-09-03 Yanmar Co Ltd SHIP POWER GENERATION SYSTEM
CN109854725A (zh) * 2019-04-02 2019-06-07 哈尔滨广瀚动力传动有限公司 一种应用于shrt机组的变速离合器的输出轴的布置形式

Also Published As

Publication number Publication date
SE396339B (sv) 1977-09-19
JPS50107688A (en, 2012) 1975-08-25
SE7501098L (en, 2012) 1975-08-04
NL7500087A (nl) 1975-08-05
FR2259748B3 (en, 2012) 1977-10-14
ES434101A1 (es) 1976-12-01
FR2259748A1 (en, 2012) 1975-08-29
DD116177A5 (en, 2012) 1975-11-12

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